Control mechanism



Oct. 5, 1954 Filed Oct. 5l. ,1952

R. LAPSLEY CONTROL MECHANISM 2 Sheets-Sheet 1 ROBERT LAPSLEY ATTYS.

R. LAPsLr-:Y 2,690,714

CONTROL MECHANISM Oct. 5, 1954 Filed Oct. 31, 1952 2 Sheets-Sheet 2 IN V EN TOR. ROBERT LAPSLEY l2 BY W y ATTYS.

Patented Oct. 5, 1954 CONTROL MECHANISM Robert Lapsley, Buchanan, Mich., assignor to Clark Equipment Company, Buchanan, Mich., la corporation of Michigan Application October 31, 1952, Serial No. 318,035

(Cl. S-38) 4 Claims.

My present invention relates generally to control mechanisms, and, more particularly, is directed to a displacement adjusting and pressure safety control mechanism for variable displacement iiuid pumps.

It is an object of my present invention to provide a control mechanism whereby the displacement of a variable displacement fluid pump may be Varied selectively.

It is another object of my present invention to provide a control mechanism which serves to actuate the displacement control plunger of a conventional variable displacement fiuid pump whereby the displacement of the latter may be varied selectively.

It is a further object of my present invention to provide a control mechanism, as noted, wherein the displacement of the pump may be preselected within the capacity of the pump.

In the accomplishment of the above objects, I contemplate the provision of a control mechanism comprising a housing adapted to be secured to the housing of a conventional variable displacement iiuid pump. Sliolably mounted in the control housing is a piston which abuts the displacement control plunger of the pump. A slidable valve is mounted in the piston and has passageway means formed therein. In addition, fluid passageway means are formed in the piston and the control housing and have communication with the suction and dischargel ports of the pump. n

The valve and passageway means are so arranged that through movement of the valve, the pump discharge port may be placed in communication with one or the other of the ends of the piston. As a result, the piston may be shifted relative to the control housing for effecting actuation oi the pump displacement control plunger. Thus, a change in displacement of the pump is conditioned by movement of the valve, after which an actual change in displacement is automatically effected by movement of the piston.

It is a feature of my present invention that the valve is of an articulated construction so as to prevent deflection thereof that would cause binding during movement of the valve.

It is a still further object of my present invention to provide a control mechanism, as described, wherein a safety valve assembly is embodied for automatically returning the pump to a position of slightly greater than zero displacement, when the pressure of fluid at the discharge port thereof exceeds a predetermined value.

I propose, in the accomplishment of the last noted object, the provision oi a pressure actuated safety valve which is associated with the pump discharge port and the control mechanism valve. When the pressure of the fluid at the discharge port of the pump exceeds the predetermined value, the safety valve is actuated permitting the iiuid under pressure to act on the control valve for returning the latter, the piston, the displacement control plunger, and the pump to their normal positions wherein the displacement -of the pump is slightly greater than zero.

Now, in order to acquaint those skilled in the art with the manner of constructing and using control mechanisms in accordance with the principles of my present invention, I shall describe in connection with the accompanying drawings. a preferred embodiment of my invention.

In the drawings:

Figure 1 is a vertical sectional View of the pump displacement adjusting and pressure safety control mechanism of my present invention;

Figure 2 is an end elevational view of the control mechanism of Figure 1 with portions being broken away and shown in section; and

Figure 3 is a general horizontal view of a portion ci the control mechanism shown in Figure 2.

Referring now to the drawings, there is indicated generally by the reference numeral I a variable displacement uid pump which comprises a housing 2 having an axially extending pilot .portion 3. An axially extending pump displacement control plunger 4 is mounted for sliding movement in the housing 2, centrally of the pilot portion 3. Axial threaded openings 5, a fluid `discharge port 6, and a uuid suction port 'I are also formed in the housing 2. The operation of the pump I is adapted to be regulated by lmeans of the pump displacement adjusting and pressure safety control `mechanism of my present invention, indicated generally by the reference numeral II. The control mechanism II comprises a housing I2 which is secured to the pump housing 2 by bolts 8 threaded into openings 5. Suitable seals 9, I `and I0 `are provided about the pilot 3 and ports 6 and 1, between the housings 42 and I2, to prevent the leakage of uid therepast.

A cylindrical opening I3 is formed 4in the control mechanism housing l2 and at one end iits about the pilot portion 3 for ypositively locating housing I2 relative to housing 2. Disposed in the cylinder I3 is a displacement regulating piston Iii which normally abuts a boss t5. Cylinder end chambers IB and I'I are dened at the ends of the piston lli. In Vthis position of the piston i4, the pump I is set a minimum displacement, i. e.

slightly greater than Zero displacement. Since fluid is required to lubricate the moving elements of the pump I and to eect actuation of the displacement regulating piston I4, the displacement of the pump I is not, and cannot be, permitted to reach zero. The pump I must be so regulated that, under all conditions of operation, at least a small amount of uid is delivered at the discharge port 6.

Movement of the piston I4 and plunger 4 to the left, as viewed in Figure 1, increases the displacement of the pump I and a corresponding return of the piston I4 and plunger 4 toward the right decreases the displacement of the pump I. I shall now describe in detail the means by which movement of the piston I4 is eiected.

A central axial opening I8 is formed in the piston I 4 and disposed therein for sliding movement is a piston actuator slide valve I9. A central axial opening is formed in the slide valve I9 which opening 20 communicates, through radial ports 2I and 22, with annular grooves 23 and 24 formed in the outer periphery of the valve I9. The valve I9 is also formed with an annular groove 25, centrally of the grooves 23 and 24, which communicates with a radial uid passageway 26 formed in the piston I 4. At the outer end of the passageway 26, an annular groove 21 is formed which communicates with a radial passageway 28 in the housing I2. The passageway 28 communicates with the pump pressure port 6 through a passageway 29.

Three additional radia1 fluid passageways 30, 3| and 32 are formed in the piston I4 and at their inner ends, communicate with opening I8. The passageways 30 and 3I communicate respectively with cylinder end chambers I6 and I1 through axial passageways 33 and 34. The passageway 32, at its outer periphery, communicates with an annular groove 35 formed in the piston I4. The groove 35 in turn communicates with a radial passageway 36 which intersects an axial passageway 31 communicating with pump suction port 1.

If it is desired to increase the displacement of the pump I from a minimum, the piston actuator slide valve I9 is moved to the left toward pump I. As a result of such movement of the valve I9, fluid under pressure is delivered to the cylinder end chamber I6, from the pump pressure port 6, through passageways 29 and 28, groove 21, passageway 26, groove 25, and passageways 3l and 34. Simultaneously, cylinder end chamber I1 is placed in communication with the pump suction port 1 through passageways 31 and 36, groove 35, passageway 32, openings I8 and 20, port 22, groove 24, and passageways 30 and 33.

The fluid under pressure, entering the chamber I 6, urges the piston I4 to the left thereby moving the plunger 4 to the left which increases the displacement of the pump I. The piston I4 will move to the left until the passageways 30 and 3| are shifted out of alignment with the grooves 24 and 25.

If it is desired to decrease the displacement of the pump I, the piston actuator slide valve I9 is moved to the right. As a result of such movement of valve I 9, fluid under pressure is delivered to the cylinder end chamber I1, from the pump discharge port 6, through passageways 29 and 28, groove 21, passageway 26, groove 25, and passageways 30 and 33. Simultaneously, cylinder end chamber I 6 is placed in communication with the pump suction port 1 through passageways 31 and 36, groove 35, passageway 32, openings I8 and 20, port 2I, groove 23, and passageways 3I and 34.

The uid under pressure, entering the chamber I1, urges the piston I4 to the right thereby permitting the plunger 4 to move to the right which decreases the displacement of the pump I. The piston I4 will move to the right until the passageways 30 and 3l are shifted out of alignment with the grooves 25 and 23. It is to be understood from the foregoing description that the displacement of the pump I may be adjusted in an infinite number of steps, within the capacity of the pump, by suitably regulating the slide valve I9.

Axially aligned with the central opening I8 in the piston I4, and formed in the housing I2, is an opening 38 in which are disposed slide valves 39 and 4D interconnected articulatively at 4I. The slide valve 39 is connected articulatively at 42 with the slide valve I9. Since the valves I9, 39, and 40 are interconnected articulatively, precise alignment of these valves is rendered unnecessary and the latter are balanced against fluid forces. The slide valve 39 is formed with an annular groove 43 and the slide valve 40 is formed with an annular groove 44. The opening 38 has communication with the passageway 31 through spaced radially extending passageways 45 and 46.

Ax axial opening 41 is formed in the housing I2 below the openings I8 and 38. The opening 41 at one end communicates with fluid passageway 28 and at its other end is closed by a closure and adjusting bolt and nut assembly 48. A radial passageway 49 connects the opening 41 with the passageway 29 and radial passageways 50 and 5I interconnect the openings 38 and 41 for a purpose to be hereinafter described in detail.

Disposed in the opening 41 is a safety valve 52 which has an axially extending nose portion 53 that projects into passageway 28. An annular groove 54 is formed in the valve 52 as is a central opening 55 which opens, through ports 56, into the opening 41 at the nose end 53 of valve 52. Extending into the opening 55 in valve 52 is a coil spring 51. The force exerted by the spring 51 may be varied by the adjusting means 48.

Now, with the elements of the pump displacement adjusting and pressure safety control mechanism I I in the positions shown in Figure l. fluid under pressure seeping past the valves I9 and 39 from the cylinder end chamber I6 is returned through groove 43 and passageways 45 and 31 to the pump suction port 1. The opening 38 is also placed in communication with the pump suction port 1 through passageways 50, pressure safety valve opening 41, passageway 5I, groove 44, and passageways 46 and 31. By normally maintaining the opening 38 in communication with the pump suction port 1, free movement of the valves I9, 39 and 40 is permitted. In addition, fluid under pressure seeping past the nose portion 53 of safety valve 52 is returned to the pump suction port 1 through ports 56, opening 55, passageway 5I, groove 44, and passageways 46 and 31. Since the safety valve opening 41 is normally in communication with the pump suction port 1, free movement of the valve 52 is permitted when line pressure exceeds a safe value. A suitable seal 58 is interposed between valve 40 and opening 38 for preventing oil leakage outwardly of housing I2. A similar seal 59 is interposed between safety valve 52 and opening 41 for preventing oil leakage outwardly of housing I2.

Let us :suppose now that the .pump il isset at maximum displacement and the pressure .of .the fluid delivered at the pump pressure port 6 :exceeds a predetermined safe value. This pressure, iiowing through passageways 2i! and 28, will act on the nose end 53 of the safety valve V52 for urging the latter to the right against the force of spring el. Upon movement of the valve 52 Ato the right, the opening 3S intermediate of the valves 3s and s is placed in communication with the pump pressure port v6 through passageway 50, groove 54 in valve 52, and passageways 49 and 2B. 'This uid under pressure serves to force the valve di) to the right thereby returning it and the valves i9 and 3:13 to a position causing the displacement of the pump l to return toa minimum value. As the pressure of the iluid delivered at the pump pressure port 6 drops, the spring 5l will return the safety valve 52 to the position shown in Figure 1 and free movement of the actuating valves I9, 39 and 40 will again be permitted. The pressure at which the safety valve 52 will be actuated may be varied by adjusting the -bolt and nut assembly 55S.

The valve iis has pivotally mounted to its outer end, by means of a pin le, the one leg of a bell crank lll. The bell crank ll, at the junction of its legs, is pivotally mounted by means of a pin 'I2 to the housing i2. The other leg of the bell crank 'il has pivotally mounted thereto, by means f a pin i3, a frame member which has an opening i formed therein. Mounted at the end of the frame member M for limited relative movement is a sleeve member 'i6 having an enlarged end head Si). The sleeve it is suitably secured to an actuator rod 7i and is maintained in position by means of a bolt 8i. rThe sleeve member 'E6 may be adjusted lengthwise of the rod Tl and may be locked in any predetermined position by the nut 8|. A spring 'it is disposed within the opening 'i5 in the frame member 'Ni and tends to normally maintain the sleeve member 'i6 in the position shown in Figure 2.

The aforedescribed mounting of the actuator rod 'il to the valve iii permits the valve 40 to move to the right for returning the valves I9 and 39 to a position causing the displacement oi the pump l to return to a minimum value, even though the actuator rod i1 may be held in a maximum displacement position, since the frame member 1d may move relative to the sleeve member 16 against the pressure of spring 18. At such time as the iluid pressure drops to a normal value and the safety valve 52 returns to the position shown in Figure 1, the spring i8 will cause the frame member 'ifi to return to the position shown in Figure 2, moving the pump elements again to a maximum displacement position.

Now, while have shown and described what I believe to be a preferred embodiment of my present invention, it will be understood that various rearrangements and modiications may be made therein without departing from the spirit and scope oi my present invention.

I claim:

1. For use with a variable displacement pump having a housing, suction and discharge ports, and a displacement control plunger, a control mechanism therefor comprising a housing secured to the pump housing, a piston opening formed in said control housing, a piston slidably mounted in said piston opening and having abutting engagement with the displacement control plunger, a valve opening formed in said piston, rst passageway means formed in said control housing .and communicating with the :discharge port, second passageway means formed in said piston and communicating with said first passageway means, third passageway means formed 5in said .piston and communicating with said valve opening and one end of said piston opening, fourth passageway means formed in said .piston and communicating with said valve opening and the :other end of said piston opening, a valve slidable in said valve opening, groove means formed in said valve, said valve when selectively actuated being adapted -to increase the displacement of the pump by placing the ydischarge port in communication with the one end of Vsaid piston ythrough said rst and second passageway means, said groove means, and said third passageway means, and said valve when selectively `actuated being adapted to decrease the displacement of the pump by placing the discharge port in communication with the other end of said piston through said iirst and second passageway means, said groove means, and said fourth passageway means.

2. For use with a 'variable displacement pump having a housing, suction and discharge ports, and a displacement control plunger, a control mechanism therefor comprising a housing secured to the pump housing, a piston opening formed in said control housing, a piston slidably mounted in said piston opening and having abutting engagement with the displacement control plunger, a valve opening formed in said piston, rst passageway means formed in said control housing and communicating with the discharge port, second passageway means formed in said piston and communicating with said first passageway means, third passageway means formed in said piston and communicating with said valve opening and one end of said piston opening, fourth passageway means formed in said piston and communicating with said valve opening and the other end of said piston opening, fifth passageway means formed in said control housing and communieating with the suction port, sixth passageway means formed in said piston and communicating with said fifth passageway means, a Valve slidable in said valve opening, groove means formed in said valve, seventh passageway means formed in said Valve, said valve when selectively actuated being adapted to increase the displacement of the pump placing the discharge port in communication with the one end of said piston through said first and second passageway means, said groove means, and said third passageway means while simultaneously placing said suction port in communication with the other end of said piston through said fifth and sixth passageway means, said valve opening and said seventh and fourth passageway means, and said valve when selectively actuated being adapted to decrease the displacement of the pump by placing the discharge port in communication with the said other end of said piston through said first and second passageway means, said groove means, and said fourth passageway means while simultaneously placing said suction port in communication with the said one end of said piston through Said fifth and sixth passageway means, said valve opening, and said seventh and third passageway means.

3. The combination of claim 2 wherein said valve is adapted to be positioned in any one of a plurality of positions whereby the displacement of the pump may be set at any predetermined point within the capacity of the pump, and Wherein said piston moves in response to movement of said valve until communication is interrupted between said groove and both said third and fourth passageways.

4. The combination of claim 2 including a secondary safety valve opening formed in said control housing, eighth passageway means formed in said control housing and communicating with said valve and said secondary safety valve opening, ninth passageway means formed in said control housing and communicating with said secondary safety valve opening and said rst passageway means, a secondary safety valve disposed in said secondary safety valve opening and projecting into said first passageway means, an an- 15 nular groove formed in said safety valve, and the fluid undei` pressure acting on the end of said safety Valve in said rst passageway means References Cited in the le of this patent UNITED STATES PATENTS Number Name Date 2,280,190 Ernst Apr. 21, 1942 2,284,897 Harrington June 2, 1942 2,298,359 Ernst Oct. 13, 1942 2,471,860 Brigham May 3l, 1949 

